EP1012479B1 - Turbine pump with improved efficiency for motor vehicle fuel tank - Google Patents

Turbine pump with improved efficiency for motor vehicle fuel tank Download PDF

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Publication number
EP1012479B1
EP1012479B1 EP98943943A EP98943943A EP1012479B1 EP 1012479 B1 EP1012479 B1 EP 1012479B1 EP 98943943 A EP98943943 A EP 98943943A EP 98943943 A EP98943943 A EP 98943943A EP 1012479 B1 EP1012479 B1 EP 1012479B1
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EP
European Patent Office
Prior art keywords
fact
pump according
blades
rotor
vanes
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Expired - Lifetime
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EP98943943A
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German (de)
French (fr)
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EP1012479A1 (en
Inventor
Anne Stathopoulos
Nicolas Résidence Les Chauvelles JOURDAIN
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Marwal Systems SAS
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Marwal Systems SAS
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Publication of EP1012479A1 publication Critical patent/EP1012479A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/188—Rotors specially for regenerative pumps

Definitions

  • the present invention relates to the field of pumps turbines for pumping fuel into a vehicle tank automobile.
  • these pumps include a housing which houses an electric drive motor and a pumping assembly driven by this engine and located at the base of said housing.
  • the main purpose of the present invention is to provide a new pump to improve efficiency compared to known pumps.
  • a turbine pump in particular for fuel tank of motor vehicle, comprising a stator housing and a rotor blades rotatably mounted relative to the housing and defining a path of pressure and flow rise between an inlet and an outlet, characterized in that the rotor has two annular series of blades concentric radially inner and radially outer respectively, to define a fuel path alternately passing through the passages defined by the radially internal vanes and by the passages defined by the radially outer vanes so that this path follows a generally helical configuration supported by an envelope annular, the two series of blades being arranged respectively radially on the inside and on the outside of a ring, the series of blades radially internal ensuring the connection between the inner periphery of the ring and the periphery of a central plate so that these vanes define an annular series of passages passing through the rotor according to its thickness, and closed at the periphery, while a second ring
  • the passages formed by the rotor cooperate with auxiliary channels formed in the stator and which has low walls inclined to a radial direction so to guide the fuel between the passages defined by the vanes radially internal and the passages defined by the radially external vanes.
  • the pitch of the walls can be different from that of the blades forming the passages in the rotor.
  • auxiliary channels provided with walls in two cups respectively disposed on either side of the rotor.
  • the walls provided on the two cups are respectively crossed between them.
  • the two sets of rotor blades are curved and tilted in directions respectively opposite from one series to another
  • the pump illustrated in the appended figures includes a stator 100 and a rotor 200.
  • the stator 100 is formed by a ring 110 sandwiched between two flanges or cups 120, 130 respectively upper and inferior.
  • the stator 100 thus defines a circular chamber centered on a 0-0 axis capable of receiving the rotor 200 rotating around this 0-0 axis.
  • the direction of rotation of the rotor 200 is referenced S.
  • La ring 110 and the cups 120 and 130 are fixed together by all appropriate means.
  • the rotor 200 is formed by a circular plate 210 of which the thickness is equal to the clearance close to the thickness of the ring 110 and the largest external radius is equal to the play near the internal radius of the ring 110.
  • the plate 210 is rotated about the axis O-O by all appropriate means.
  • the plate 210 is driven by a electric motor (not shown in the appended figures) whose shaft outlet is in engagement with the hub of the plate 210.
  • the plate 210 is provided in its center with a non-symmetrical structure of revolution 240. It it is an orifice delimited by two diametrically opposite planes connected between them by their ends by semi-cylindrical caps, according to the particular representation given in the appended figures. However this particular representation is in no way limiting.
  • At least one of the cups 120, 130 must be provided with a central through hole to allow access and training of this structure 240.
  • the plate 210 is provided with two annular series of blades concentric 220 and 230.
  • the vanes 220 and 230 are thus arranged according to two annular assemblies respectively internal and external defining each series of passages 222, 232 crossing the following plate 210 a general direction corresponding to its thickness.
  • the two sets of blades 220 and 230 are arranged respectively radially on the inside and on the outside of a ring 250.
  • the vanes 230 protrude in a generally radial direction on the outer periphery of the ring 250.
  • the vanes 220 provide the connection between the inner periphery of the ring 250 and the periphery of the plate central 210.
  • the vanes 220 define an annular series of passages 222 passing through the rotor 200 according to its thickness, but closed at periphery.
  • the rotor 200 is also provided with an outer ring 260 disposed radially on the outside of the vanes 230.
  • the vanes 230 provide the connection between the periphery the outer ring 250 and the inner periphery of the ring 260 and the vanes 230 define an annular series of passages 232 passing through the rotor 200 depending on its thickness, but also closed radially towards the outside by the ring 260.
  • Such an external ring 260 allows good mechanical strength for the blades 230 and limits the stresses applied to the ring 110.
  • the dimensions of the ring 110 and cups 120 and 130 must be adapted accordingly so that channels 122, 132 formed in the cups 120, 130, the structure and function will be specified later, be arranged in look at passages 222, 232 formed by vanes 220 and 230.
  • the two rings 250 and 260 can each have a radial dimension of the order of 0.8mm.
  • these blades 220 and 230 are adapted for impose on the fuel put into circulation and under pressure inside the pump, a generally helical path supported by an envelope annular and passing successively and alternately through passages internal 222 and by external passages 232.
  • This annular envelope of the path followed by the fuel is defined, for its portion radially internal by the passages 222 delimited by the radially internal vanes 220, for its radially external portion by the passages 232 delimited by the radially outer vanes 230, and for its connection zones between these radially internal and external portions, by semi-annular auxiliary channels 122, 132 delimited respectively by the cups 120 and 130, on their opposite faces, directed towards the rotor 200.
  • the cross section of the channels 122, 132 can be the subject of various variants.
  • these channels 122, 132 have a cross section in the form of half-ellipse, i.e. it has a continuous curvature, of radius decreasing, from the middle of the bottom of said channels to the free edges of these coinciding with the internal surface of the cups 120, 130 (by opposition to known channels whose cross section is delimited by a rectilinear base segment extended on both sides by sectors of circles).
  • the cross section of the channels 122, 132 is symmetrical preference with respect to a median plane orthogonal to this internal surface of the cups 120, 130.
  • the radially internal radius of the channels 122, 132 is complementary to the smallest radially internal radius of the vanes 220, while the radially outer radius of the channels 122, 132 is complementary to the larger radially outer radius of the blades 230.
  • An inlet 134 crosses in a general direction axial the lower cup 130 and opens onto one end of the channel 132, while an outlet 124 crosses in a general direction axial the upper cup 120 and opens onto the other end of the channel 122.
  • the inlet ports 134 are inclined on the order of 30 ° to 75 °, very preferably on the order 53 ° to an axis orthogonal to the axis of rotation O-O, while the outlet orifices 124 are inclined on the order of 10 ° to 45 °, very preferably of the order of 15 ° to 20 ° relative to an axis orthogonal to the axis of rotation O-O.
  • the aforementioned inclination of the inlet orifice 1345 can in particular be observed in Figure 19.
  • the channel 132 formed in the lower cup 130 has an initial section 1320 of section decreasing leading to a transition zone referenced 1321, followed of a portion of constant section 1322, to finish with a portion of decreasing section 1323.
  • the channel 122 has an initial section section declining 1220, followed by a portion of constant section 1221, to finish with a decreasing section 1222.
  • the sections 1221 and 1322 may have a slightly cross section decreasing when we go respectively to sections 1220 and 1323
  • channel 132 designed to conduct fuel from radially external passages 232 towards the radially internal passages 222 has a cross section greater than that of the channel 122 formed in the upper cup 120.
  • channels 122, 132 cover a sector angular less than 360 ° around the axis O-O.
  • the useful sections 1224, 1324 of these semi-annular canals 122 and 132 this is ie the sections in which the pressure rise of the fuel, cover an angle of around 270 ° around the axis of rotation 0-0.
  • basins 1201, 1202, 1203 and 1204, 1301, 1302, 1303 and 1304 formed in hollow in the internal surfaces of each cup 120, 130.
  • These basins are designed to be pressurized with fuel from channels 122, 132 to form hydrostatic bearings supporting the rotor 200 in its rotation around the axis O-O.
  • the helical-annular path is shown schematically in Figure 3 and partially illustrated in more detail in Figure 4.
  • the fuel which enters the pump chamber through entry 134 first reaches channel 132 formed in the cup lower 130, and from there gains a passage 222 formed by the vanes 220, then the channel 122 formed in the upper flange 120, a passage 232 formed by the external vanes 230, the channel 132 formed by the flange lower 130 and then again a passage 222 and so on until reach exit 124.
  • the cups 120 and 130 are preferably provided on their external surface of indexing or polarizing means.
  • Such means are shown schematically in the appended figures in the form of at least one groove 126, 136 formed in the outer periphery of the cups 120, 130, which grooves are intended to be aligned during assembly and the relative immobilization of the cups 120 and 130 to receive a key.
  • the ring 110 is preferably provided with a groove external 112 intended to be aligned with the grooves 126, 136 for receive the aforementioned key.
  • the ring 110 can be integrated into one of the cups 120, 130.
  • auxiliary channels 122 and 132 provided in the cups 120 and 130 of the stator 100 has walls 127, 137 inclined to a radial direction. These low walls 127, 137 impose thus to fuel a path which passes successively through pairs of radially internal and radially external passages 222 and 232.
  • the walls 127 and 137 are formed of walls planes parallel to the axis of rotation O-O and inclined with respect to a radial direction, as previously indicated.
  • grooves 128, 138 suitable for guide the fuel between the passages 222 defined by the blades radially internal 220 and the passages 232 defined by the blades radially external 230.
  • the cross section of the grooves 128, 138 can be the subject of many variations depending on the geometry of the bottom wall thereof. It is thus possible to design grooves 128, 138 of triangular cross section or semi circular or rounded, in particular.
  • the grooves 128 and 138 have a straight cross section rectangular, bounded by a base surface perpendicular to the axis of O-O rotation and two sides defined by low walls 127 or 137.
  • each of the auxiliary channels 122 and 132 is fitted with such low walls 127, 137.
  • the pitch of the walls 127, 137 may be identical to that of the blades 220, 230. However, this equality of pitch is not compulsory in the scope of the present invention.
  • low walls 127, 137 provided on the two cups 120, 130 are respectively crossed between them, preferably substantially at 45 °, to ensure correct fuel guidance. So if we observe the low walls 137 provided on the lower cup 130, in a direction going from the upper cup 120 to the lower cup 130, the low walls 137 deploy anti-trigonometrically when moving radially outward. Conversely, the low walls 127 provided on the upper cup 120 observed in the same direction deploy in a trigonometric direction when one moves radially towards outside.
  • the low walls 127 guide the fuel from the outlet of a passage 222 radially internal, towards the entrance of passage 232 radially external, while the low walls 137 guide the fuel of the exit from a passage 232 radially external, towards the entry of a passage 232 radially internal.
  • the top of the walls 127, 137 is not coplanar with the surfaces internal cups 120, 130, but set back from these surfaces internal, for example with an interval of the order of 0.1 mm, as can be seen for example in Figure 17.
  • the blades concentric 220 and 230 are curved and tilted in directions respectively opposite from one series to another.
  • the internal vanes 220 deploy in the S direction when moving from the upper cup 120 towards the cup lower 130.
  • the external vanes 230 are deployed in the opposite direction to S, i.e. clockwise, when moving in the same way from the upper cup 120 towards the lower cup 130.
  • the inclination of the blades is reversed if one of the directions of rotation S of the rotor or propeller, is reversed.
  • vanes 220, 230 have their concavity directed towards the front, in reference to the direction of movement S of the rotor 200.
  • the lower surfaces 2200, 2300 and upper surfaces 2202, 2302 of the vanes 220 and 230 are preferably defined by rectilinear generators, radial with respect to the axis of rotation O-O and which are based on curves when said generators are displaced along the axis O-O.
  • leading edges of the vanes 220 and 230 are referenced 2204 and 2304, while the trailing edges of same blades 220 and 230 are referenced 2206 and 2306.
  • leading edges 2204 are located on the lower surface of rotor 200, while trailing edges 2206 are located on the surface upper part of rotor 200.
  • trailing edges 2206 are located on the surface upper part of rotor 200.
  • leading edges 2304 are located on the upper surface of the rotor 200, while the trailing edges 2306 are located on the bottom surface of the rotor 200.
  • the lower surface 2200 and 2300 and the upper surface 2202 and 2302 have identical curvatures.
  • the lower surface 2200 and the upper surface 2202 of the blades internal 220 are identical to each other, while the lower surface 2300 and the upper surfaces 2302 of the external vanes 230 have curvatures identical to each other, but of radius different from those of lower surface 2200 and upper surface 2202 of the internal vanes 220 above.
  • the internal vanes 220 and the external vanes 230 have identical thicknesses "e" at their leading edge 2204, 2304 and at their trailing edge 2206, 2306 (We mean here by "thickness” the transverse dimension "e” of the vanes 220, 230 considered in a plane perpendicular to the axis of rotation O-O).
  • the internal vanes 220 have identical thicknesses e1 in terms of their leading edge 2204 and at their trailing edge 2206.
  • the external blades 230 have identical thicknesses e2 in terms of their leading edge 2304 and at their trailing edge 2306, but the thickness e2 of the external vanes 230 is different (greater) from that e1 of the internal vanes 220.
  • the lower surface 2200, 2300, at the edge 2204, 2304 is preferably inclined at an angle between 130 ° and 170 ° relative to a plane perpendicular to the axis of rotation O-O, while the same lower surface 2200, 2300 at the trailing edge 2206, 2306 is preferably inclined on the order of 90 ° relative to a plane perpendicular to the axis of rotation O-O (i.e. the surface lower surface 2200, 2300 at the trailing edge 2206, 2306 is preferably parallel to the axis of rotation O-O).
  • leading edge 2204, 2304 of the vanes 220 and 230 is shown tapered.
  • this leading edge 2204, 2304 can be rounded off for reasons of mechanical strength.
  • the radius of such a leading edge rounding can be of the order of 0.15mm.
  • each blade 220 and 230 is defined by a constant wall thickness "e", considered in a plane perpendicular to the axis of rotation O-O. As seen on the figures, particularly in FIG. 9b, this however leads to a weakening of the vanes 220, 230 at the leading edge 2204, 2304.
  • the blades have different thicknesses "e3" and "e4" (considered in a plane perpendicular to the axis of rotation), respectively at the leading edge and at the trailing edge.
  • this dimension Y is of the order of 0.3 mm.
  • the blades 220, 230 have widths "L" (considered parallel to the axis of rotation O-O) identical and constant over their entire radial extension. This width L of the vanes 220, 230 is equal to the thickness of the rotor 200.
  • the internal vanes 220 and the external vanes 230 have preferably even radial extension.
  • the pump according to the present invention allows to significantly improve the yield obtained.
  • the pump according to the present invention achieves a yield of around 24%.
  • all the parts of the pump namely the cups 120 and 130, the ring 110 and the rotor 200, are made of plastic.
  • the cups 120, 130 can be made of metal, the rotor 200 at least being made of plastic.
  • reference 1380 illustrates an orifice of degassing through the lower cup 130 and opening into the channel 132 downstream of the inlet 134.
  • channels 222 and 232 formed between the pairs of adjacent blades 220, 230 are each formed by a pair of complementary growths 310, 320 linked respectively to each of the molding shells.
  • these protuberances 310, 320 are preferably adapted for define joint planes located on the main surfaces of the rotor, orthogonal to the axis of rotation O-O.
  • the protuberances 310, 320 are preferably adapted to define joint planes P1, P2 which respectively coincide with one with the leading edge generator located in the P3 plane passing through the axis O-O tangent with this leading edge 2204, 2304 and the other with the edge leak 2206, 2306.
  • the vanes 220, 230 and the channels 222, 232 formed by them are preferably dimensioned so that the vertices 312, 322 of the protrusions 310, 320 have a minimum width La of the order of 0.5 mm, with a minimum draft angle of 6 °.
  • the interval I1 between two adjacent blades 220 at the level of the trailing edge 2206 can be of the order of 2.52mm, while the interval I2 between two radially external vanes 230, at the trailing edges 2306 is around 2.94mm, the projection I3 and I4 of the upper surface 2202 and 2302 of the vanes 220 and 230, on a plane orthogonal to the axis O-O being respectively of the order of 1mm and 1.84mm.
  • a number of radially internal vanes 220 is provided equal to the number radially external vanes 230.
  • this arrangement is not imperative.
  • the number of internal vanes 220 can be different from the number of external vanes 230.
  • the number both internal 220 and external vanes 230 is equal to an integer.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)

Description

La présente invention concerne le domaine des pompes turbines pour le pompage de carburant dans un réservoir de véhicule automobile.The present invention relates to the field of pumps turbines for pumping fuel into a vehicle tank automobile.

On a déjà proposé de nombreuses pompes à cet effet. Des exemples de telles pompes connues sont décrits dans les documents FR-A-2 714 121, FR-A-2 711 741, FR-A-2 713 714, FR-A-2 720 118, FR-A-2 722 536, FR-A-2 685 937 et EP-A-0 735 271.Many pumps have already been proposed for this purpose. of the examples of such known pumps are described in documents FR-A-2 714 121, FR-A-2 711 741, FR-A-2 713 714, FR-A-2 720 118, FR-A-2 722 536, FR-A-2 685 937 and EP-A-0 735 271.

D'une façon générale ces pompes comprennent un carter qui loge un moteur électrique d'entraínement et un ensemle de pompage entraíné par ce moteur et situé à la base dudit carter.Generally these pumps include a housing which houses an electric drive motor and a pumping assembly driven by this engine and located at the base of said housing.

Cependant à la connaissance des inventeurs aucune des pompes jusqu'ici proposées ne donne totalement satisfaction, notamment quant au rendement.However, to the knowledge of the inventors, none of the pumps so far offered are not entirely satisfactory, in particular as for performance.

Le but principal de la présente invention est de proposer une nouvelle pompe permettant d'améliorer le rendement par rapport aux pompes connues.The main purpose of the present invention is to provide a new pump to improve efficiency compared to known pumps.

Ce but est atteint dans le cadre de la présente invention, grâce à une pompe turbine, notamment pour réservoir de carburant de véhicule automobile, comprenant un boitier formant stator et un rotor à aubes monté à rotation par rapport au boitier et définissant un trajet de montée en pression et d'écoulement entre une entrée et une sortie, caractérisée par le fait que le rotor possède deux séries annulaires d'aubes concentriques respectivement radialement interne et radialement externe, pour définir un trajet de carburant passant alternativement par les passages définis par les aubes radialement internes et par les passages définis par les aubes radialement externes de sorte que ce trajet suive une configuration généralement en hélice s'appuyant sur une enveloppe annulaire, les deux séries d'aubes étant disposées respectivement radialement sur l'intérieur et sur l'extérieur d'un anneau, la série d'aubes radialement interne assurant la liaison entre la périphérie intérieure de l'anneau et la périphérie d'un plateau central de sorte que ces aubes définissent une série annulaire de passages traversant le rotor selon son épaisseur, et fermés en périphérie, tandis qu'un deuxième anneau est disposé sur l'extérieur de la série d'aubes externes de sorte que celles-ci définissent une série annulaire de passages traversant le rotor selon son épaisseur, et fermés en périphérie.This object is achieved in the context of the present invention, thanks to a turbine pump, in particular for fuel tank of motor vehicle, comprising a stator housing and a rotor blades rotatably mounted relative to the housing and defining a path of pressure and flow rise between an inlet and an outlet, characterized in that the rotor has two annular series of blades concentric radially inner and radially outer respectively, to define a fuel path alternately passing through the passages defined by the radially internal vanes and by the passages defined by the radially outer vanes so that this path follows a generally helical configuration supported by an envelope annular, the two series of blades being arranged respectively radially on the inside and on the outside of a ring, the series of blades radially internal ensuring the connection between the inner periphery of the ring and the periphery of a central plate so that these vanes define an annular series of passages passing through the rotor according to its thickness, and closed at the periphery, while a second ring is arranged on the outside of the series of external vanes so that these define an annular series of passages passing through the rotor according to its thickness, and closed at the periphery.

Selon un autre aspect important de l'invention les passages formés par le rotor coopèrent avec des canaux auxiliaires ménagés dans le stator et qui possédent des murets inclinés par rapport à une direction radiale afin de guider le carburant entre les passages définis par les aubes radialement internes et les passages définis par les aubes radialement externes.According to another important aspect of the invention, the passages formed by the rotor cooperate with auxiliary channels formed in the stator and which has low walls inclined to a radial direction so to guide the fuel between the passages defined by the vanes radially internal and the passages defined by the radially external vanes.

Comme on l'expliquera par la suite, le pas des murets peut être différent de celui des aubes formant les passages dans le rotor.As will be explained below, the pitch of the walls can be different from that of the blades forming the passages in the rotor.

Selon une autre caractéristique avantageuse de la présente invention, il est prévu de tels canaux auxiliaires munis de murets dans deux coupelles disposées respectivement de part et d'autre du rotor.According to another advantageous characteristic of the present invention, provision is made for such auxiliary channels provided with walls in two cups respectively disposed on either side of the rotor.

Selon une autre caractéristique avantageuse de la présente invention, les murets prévus sur les deux coupelles sont respectivement croisés entre eux.According to another advantageous characteristic of the present invention, the walls provided on the two cups are respectively crossed between them.

Selon un autre aspect important de la présente invention, les deux séries d'aubes du rotor sont incurvées et inclinées dans des sens respectivement opposées d'une série à l'autre,According to another important aspect of the present invention, the two sets of rotor blades are curved and tilted in directions respectively opposite from one series to another,

D'autres caractéristiques, buts et avantages de la présente invention apparaitront à la lecture de la description détaillée qui va suivre et en regard des dessins annexés, donnés à titre d'exemples non limitatifs et sur lesquels :

  • la figure 1 annexée représente une vue schématique en perspective éclatée des moyens essentiels d'une pompe conforme à la présente invention,
  • la figure 2 représente une seconde vue schématique en perspective éclatée, opposée à celle de la figure 1, des mêmes moyens essentiels de la pompe conforme à la présente invention,
  • la figure 3 illustre schématiquement le trajet suivi par le carburant dans la chambre de pompage,
  • la figure 4 représente une vue partielle de ce trajet,
  • la figure 5 représente une vue d'un rotor conforme à la présente invention,
  • les figures 6 et 7 représentent respectivement des vues en plan interne de coupelle inférieure et supérieure d'une telle pompe conforme à la présente invention.
  • la figure 8a représente une illustration développée sur un plan, des aubes radialement internes observées en vue latérale perpendiculairement à l'axe de rotation, selon un premier mode de réalisation de la présente invention,
  • la figure 8b représente une illustration similaire développée sur un plan, des aubes radialement externes observées en vue latérale perpendiculairement à l'axe de rotation, selon le même premier mode de réalisation de la présente invention,
  • la figure 9a représente une illustration développée sur un plan, des aubes radialement internes observées en vue latérale perpendiculairement à l'axe de rotation, selon un deuxième mode de réalisation de la présente invention,
  • la figure 9b représente une illustration similaire développée sur un plan, des aubes radialement externes observées en vue latérale perpendiculairement à l'axe de rotation, selon le même deuxième mode de réalisation de la présente invention,
  • la figure 10 représente une vue partielle dans un plan perpendiculaire à l'axe de rotation des aubes conformes à la présente invention,
  • la figure 11 représente une vue similaire dans un plan perpendiculaire à l'axe de rotation, de murets conformes à la présente invention, prévus sur le stator de la pompe,
  • la figure 12 illustre une variante de profil d'aube conforme à la présente invention,
  • les figures 13a et 13b représentent des vues similaires aux figures 8 et 9 respectivement d'aubes radialement internes et radialement externes, conformes à une variante de la présente invention,
  • les figures 14 et 15 illustrent schématiquement le trajet de filets de carburant dans la chambre de pompage, respectivement en l'absence de murets et en présence de murets conformes à la présente invention,
  • la figure 16 illustre schématiquement la structure d'un outil de moulage conforme à la présente invention, et
  • les figures 17, 18 et 19 représentent trois vues en coupe transversale d'une coupelle inférieure conforme à la présente invention selon les vues illustrées respectivement sous les références XVII, XVIII et XIX sur la figure 6 (la figure 17 étant à une échelle double des figures 18 et 19).
Other characteristics, objects and advantages of the present invention will appear on reading the detailed description which follows and with reference to the appended drawings, given by way of nonlimiting examples and in which:
  • FIG. 1 appended represents a schematic exploded perspective view of the essential means of a pump according to the present invention,
  • FIG. 2 represents a second schematic exploded perspective view, opposite to that of FIG. 1, of the same essential means of the pump according to the present invention,
  • FIG. 3 schematically illustrates the path followed by the fuel in the pumping chamber,
  • FIG. 4 represents a partial view of this path,
  • FIG. 5 represents a view of a rotor according to the present invention,
  • Figures 6 and 7 respectively show internal plan views of the lower and upper cup of such a pump according to the present invention.
  • FIG. 8a represents an illustration developed on a plane, radially internal vanes observed in lateral view perpendicular to the axis of rotation, according to a first embodiment of the present invention,
  • FIG. 8b represents a similar illustration developed on a plane, radially external vanes observed in lateral view perpendicular to the axis of rotation, according to the same first embodiment of the present invention,
  • FIG. 9a represents an illustration developed on a plane, radially internal vanes observed in lateral view perpendicular to the axis of rotation, according to a second embodiment of the present invention,
  • FIG. 9b represents a similar illustration developed on a plane, radially external vanes observed in lateral view perpendicular to the axis of rotation, according to the same second embodiment of the present invention,
  • FIG. 10 represents a partial view in a plane perpendicular to the axis of rotation of the blades in accordance with the present invention,
  • FIG. 11 shows a similar view in a plane perpendicular to the axis of rotation, of walls in accordance with the present invention, provided on the stator of the pump,
  • FIG. 12 illustrates a variant of the blade profile in accordance with the present invention,
  • FIGS. 13a and 13b show views similar to FIGS. 8 and 9 respectively of radially internal and radially external vanes, in accordance with a variant of the present invention,
  • FIGS. 14 and 15 schematically illustrate the path of fuel nets in the pumping chamber, respectively in the absence of walls and in the presence of walls in accordance with the present invention,
  • FIG. 16 schematically illustrates the structure of a molding tool according to the present invention, and
  • Figures 17, 18 and 19 show three cross-sectional views of a lower cup according to the present invention according to the views illustrated respectively under the references XVII, XVIII and XIX in Figure 6 (Figure 17 being on a double scale of Figures 18 and 19).

On va tout d'abord décrire la structure générale de la pompe conforme à la présente invention.We will first describe the general structure of the pump according to the present invention.

La pompe illustrée sur les figures annexées comprend un stator 100 et un rotor 200.The pump illustrated in the appended figures includes a stator 100 and a rotor 200.

Le stator 100 est formé d'une bague 110 prise en sandwich entre deux flasques ou coupelles 120, 130 respectivement supérieur et inférieur.The stator 100 is formed by a ring 110 sandwiched between two flanges or cups 120, 130 respectively upper and inferior.

Le stator 100 définit ainsi une chambre circulaire centrée sur un axe 0-0 apte à recevoir le rotor 200 à rotation autour de cet axe 0-0. Sur les figures annexées, le sens de rotation du rotor 200 est référencé S. La bague 110 et les coupelles 120 et 130 sont fixées entre elles par tous moyens appropriés.The stator 100 thus defines a circular chamber centered on a 0-0 axis capable of receiving the rotor 200 rotating around this 0-0 axis. Sure the attached figures, the direction of rotation of the rotor 200 is referenced S. La ring 110 and the cups 120 and 130 are fixed together by all appropriate means.

Le rotor 200 est formé d'un plateau circulaire 210 dont l'épaisseur est égale au jeu près à l'épaisseur de la bague 110 et dont le plus grand rayon externe est égal au jeu près au rayon interne de la bague 110.The rotor 200 is formed by a circular plate 210 of which the thickness is equal to the clearance close to the thickness of the ring 110 and the largest external radius is equal to the play near the internal radius of the ring 110.

Le plateau 210 est entrainé à rotation autour de l'axe O-O par tous moyens appropriés. De préférence le plateau 210 est entrainé par un moteur électrique (non représenté sur les figures annexées) dont l'arbre de sortie est en prise avec le moyeu du plateau 210. Pour celà le plateau 210 est muni en son centre d'une structure non symétrique de révolution 240. Il s'agit d'un orifice délimité par deux plans diamétralement opposés reliés entre eux par leurs extrémités par des calottes semi-cylindriques, selon la représentation particulière donnée sur les figures annexées. Cependant cette représentation particulière n'est aucunement limitative. The plate 210 is rotated about the axis O-O by all appropriate means. Preferably the plate 210 is driven by a electric motor (not shown in the appended figures) whose shaft outlet is in engagement with the hub of the plate 210. For this the plate 210 is provided in its center with a non-symmetrical structure of revolution 240. It it is an orifice delimited by two diametrically opposite planes connected between them by their ends by semi-cylindrical caps, according to the particular representation given in the appended figures. However this particular representation is in no way limiting.

Bien entendu l'une au moins des coupelles 120, 130 doit être munie d'un orifice central traversant pour permettre l'accès et l'entrainement de cette structure 240.Of course at least one of the cups 120, 130 must be provided with a central through hole to allow access and training of this structure 240.

Le plateau 210 est muni de deux séries annulaires d'aubes concentriques 220 et 230. Les aubes 220 et 230 sont ainsi disposées selon deux ensembles annulaires respectivement interne et externe définissant chacun des séries de passages 222, 232 traversant le plateau 210 suivant une direction générale correspondant à son épaisseur.The plate 210 is provided with two annular series of blades concentric 220 and 230. The vanes 220 and 230 are thus arranged according to two annular assemblies respectively internal and external defining each series of passages 222, 232 crossing the following plate 210 a general direction corresponding to its thickness.

Les deux séries d'aubes 220 et 230 sont disposées respectivement radialement sur l'intérieur et sur l'extérieur d'un anneau 250. Les aubes 230 font saillie dans une direction générale radiale sur la périphérie extérieure de l'anneau 250. Les aubes 220 assurent la liaison entre la périphérie intérieure de l'anneau 250 et la périphérie du plateau central 210. Ainsi les aubes 220 définissent une série annulaire de passages 222 traversant le rotor 200 selon son épaisseur, mais fermés en périphérie.The two sets of blades 220 and 230 are arranged respectively radially on the inside and on the outside of a ring 250. The vanes 230 protrude in a generally radial direction on the outer periphery of the ring 250. The vanes 220 provide the connection between the inner periphery of the ring 250 and the periphery of the plate central 210. Thus the vanes 220 define an annular series of passages 222 passing through the rotor 200 according to its thickness, but closed at periphery.

Comme on l'a illustré sur les figures, le rotor 200 est également muni d'un anneau externe 260 disposé radialement sur l'extérieur des aubes 230. Ainsi les aubes 230 assurent la liaison entre la périphérie externe de l'anneau 250 et la périphérie interne de l'anneau 260 et les aubes 230 définissent une série annulaire de passages 232 traversant le rotor 200 selon son épaisseur, mais fermés également radialement vers l'extérieur par l'anneau 260. Un tel anneau externe 260 permet une bonne tenue mécanique pour les aubes 230 et permet de limiter les contraintes appliquées sur la bague 110. Bien entendu les dimensions de la bague 110 et des coupelles 120 et 130 doivent être adaptées en conséquence de sorte que des canaux 122, 132 formés dans les coupelles 120, 130, dont la structure et la fonction seront précisées par la suite, soient disposés en regard des passages 222, 232 formés par les aubes 220 et 230.As illustrated in the figures, the rotor 200 is also provided with an outer ring 260 disposed radially on the outside of the vanes 230. Thus the vanes 230 provide the connection between the periphery the outer ring 250 and the inner periphery of the ring 260 and the vanes 230 define an annular series of passages 232 passing through the rotor 200 depending on its thickness, but also closed radially towards the outside by the ring 260. Such an external ring 260 allows good mechanical strength for the blades 230 and limits the stresses applied to the ring 110. Of course the dimensions of the ring 110 and cups 120 and 130 must be adapted accordingly so that channels 122, 132 formed in the cups 120, 130, the structure and function will be specified later, be arranged in look at passages 222, 232 formed by vanes 220 and 230.

A titre d'exemple non limitatif, les deux anneaux 250 et 260 peuvent possèder chacun une dimension radiale de l'ordre de 0,8mm.By way of nonlimiting example, the two rings 250 and 260 can each have a radial dimension of the order of 0.8mm.

Plus précisément ces aubes 220 et 230 sont adaptées pour imposer au carburant mis en circulation et en pression à l'intérieur de la pompe, un trajet généralement en hélice s'appuyant sur une enveloppe annulaire et passant successivement et alternativement par des passages internes 222 et par des passages externes 232. Cette enveloppe annulaire du trajet suivi par le carburant est définie, pour sa portion radialement interne par les passages 222 délimités par les aubes radialement internes 220, pour sa portion radialement externe par les passages 232 délimités par les aubes radialement externes 230, et pour ses zones de liaison entre ces portions radialement interne et externe, par des canaux auxiliaires semi-annulaires 122, 132 délimités respectivement par les coupelles 120 et 130, sur leurs faces en regard, dirigées vers le rotor 200.More precisely, these blades 220 and 230 are adapted for impose on the fuel put into circulation and under pressure inside the pump, a generally helical path supported by an envelope annular and passing successively and alternately through passages internal 222 and by external passages 232. This annular envelope of the path followed by the fuel is defined, for its portion radially internal by the passages 222 delimited by the radially internal vanes 220, for its radially external portion by the passages 232 delimited by the radially outer vanes 230, and for its connection zones between these radially internal and external portions, by semi-annular auxiliary channels 122, 132 delimited respectively by the cups 120 and 130, on their opposite faces, directed towards the rotor 200.

Ces canaux 122, 132 sont visibles notamment sur les figures 6 et 7 annexées.These channels 122, 132 are visible in particular in the figures 6 and 7 appended.

La section droite des canaux 122, 132 peut faire l'objet de diverses variantes. De préférence, comme on l'a illustré sur les figures 17 et 18 notamment, ces canaux 122, 132 ont une section droite en forme de demi-ellipse, c'est à dire qu'il présente une courbure continue, de rayon décroissant, à partir du milieu du fond desdits canaux vers les bords libres de ceux-ci coïncidant avec la surface interne des coupelles 120, 130 (par opposition à des canaux connus dont la section droite est délimitée par un segment de base rectiligne prolongé de part et d'autre par des secteurs de cercles). Par ailleurs la section droite des canaux 122, 132 est de préférence symétrique par rapport à un plan médian orthogonal à cette surface interne des coupelles 120, 130.The cross section of the channels 122, 132 can be the subject of various variants. Preferably, as illustrated in Figures 17 and 18 in particular, these channels 122, 132 have a cross section in the form of half-ellipse, i.e. it has a continuous curvature, of radius decreasing, from the middle of the bottom of said channels to the free edges of these coinciding with the internal surface of the cups 120, 130 (by opposition to known channels whose cross section is delimited by a rectilinear base segment extended on both sides by sectors of circles). Furthermore, the cross section of the channels 122, 132 is symmetrical preference with respect to a median plane orthogonal to this internal surface of the cups 120, 130.

Le rayon radialement interne des canaux 122, 132 est complémentaire du plus petit rayon radialement interne des aubes 220, tandis que le rayon radialement externe des canaux 122, 132 est complémentaire du plus grand rayon radialement externe des aubes 230.The radially internal radius of the channels 122, 132 is complementary to the smallest radially internal radius of the vanes 220, while the radially outer radius of the channels 122, 132 is complementary to the larger radially outer radius of the blades 230.

Un orifice d'entrée 134 traverse dans une direction générale axiale la coupelle inférieure 130 et débouche sur une extrémité du canal 132, tandis qu'un orifice de sortie 124 traverse dans une direction générale axiale la coupelle supérieure 120 et débouche sur l'autre extrémité du canal 122. An inlet 134 crosses in a general direction axial the lower cup 130 and opens onto one end of the channel 132, while an outlet 124 crosses in a general direction axial the upper cup 120 and opens onto the other end of the channel 122.

Plus précisément pour ne pas perturber l'écoulement du carburant dans la chambre de pompage, de préférence les orifices d'entrée 134 sont inclinés de l'ordre de 30° à 75°, très préférentiellement de l'ordre de 53° par rapport à un axe orthogonal à l'axe de rotation O-O, tandis que les orifices de sortie 124 sont inclinés de l'ordre de 10° à 45°, très préférentiellement de l'ordre de 15° à 20° par rapport à un axe orthogonal à l'axe de rotation O-O. L'inclinaison précitée de l'orifice d'entrée 1345 peut notamment être observé sur la figure 19.More precisely so as not to disturb the flow of the fuel in the pumping chamber, preferably the inlet ports 134 are inclined on the order of 30 ° to 75 °, very preferably on the order 53 ° to an axis orthogonal to the axis of rotation O-O, while the outlet orifices 124 are inclined on the order of 10 ° to 45 °, very preferably of the order of 15 ° to 20 ° relative to an axis orthogonal to the axis of rotation O-O. The aforementioned inclination of the inlet orifice 1345 can in particular be observed in Figure 19.

Ainsi le carburant qui pénètre par l'entrée 134, est entrainé selon le trajet en hélice-annulaire précité et atteint l'orifice de sortie 124.Thus the fuel which penetrates by the entry 134, is entrained along the aforementioned helical-annular path and reaches the outlet orifice 124.

Plus précisément, à partir de l'entrée 134, le canal 132 formé dans la coupelle inférieure 130 possède un tronçon initial 1320 de section décroissante débouchant sur une zone de transition référencée 1321, suivie d'une portion de section constante 1322, pour finir avec une portion de section décroissante 1323. Partant de la sortie 124 taillée dans la coupelle supérieure 120, le canal 122 présente un tronçon initial de section déroissante 1220, suivi d'une portion de section constante 1221, pour se terminer par une section décroissante 1222. Selon une variante les tronçons 1221 et 1322 peuvent présenter une section légèrement décroissante lorsqu'on se dirige resepctivement vers les tronçons 1220 et 1323More precisely, from entry 134, the channel 132 formed in the lower cup 130 has an initial section 1320 of section decreasing leading to a transition zone referenced 1321, followed of a portion of constant section 1322, to finish with a portion of decreasing section 1323. Starting from the outlet 124 cut in the cup upper 120, the channel 122 has an initial section section declining 1220, followed by a portion of constant section 1221, to finish with a decreasing section 1222. According to a variant the sections 1221 and 1322 may have a slightly cross section decreasing when we go respectively to sections 1220 and 1323

Selon une autre variante de la présente invention, le canal 132 conçu pour conduire le carburant des passages 232 radialement externes vers les passages 222 radialement internes, en l'espèce le canal 132 formé dans la coupelle inférieure 130, possède une section droite supérieure à celle du canal 122 formé dans la coupelle supérieure 120.According to another variant of the present invention, channel 132 designed to conduct fuel from radially external passages 232 towards the radially internal passages 222, in this case the channel 132 formed in the lower cup 130, has a cross section greater than that of the channel 122 formed in the upper cup 120.

On notera que les canaux 122, 132 couvrent un secteur angulaire inférieur à 360° autour de l'axe O-O.Note that channels 122, 132 cover a sector angular less than 360 ° around the axis O-O.

Selon la représentation donnée sur les figures annexées, les tronçons utiles 1224, 1324 de ces canaux semi-annulaires 122 et 132, c'est à dire les tronçons dans lesquels est opérée la montée en pression du carburant, couvrent un angle de l'ordre de 270° autour de l'axe de rotation 0-0. According to the representation given in the appended figures, the useful sections 1224, 1324 of these semi-annular canals 122 and 132, this is ie the sections in which the pressure rise of the fuel, cover an angle of around 270 ° around the axis of rotation 0-0.

On notera sur les figures 6 et 7 la présence de 4 vasques 1201, 1202, 1203 et 1204, 1301, 1302, 1303 et 1304 formées en creux dans les surfaces internes de chaque coupelle 120, 130. Ces vasques sont conçues pour être mises sous pression de carburant à partir des canaux 122, 132 pour former des paliers hydrostatiques soutenant le rotor 200 dans sa rotation autour de l'axe O-O.Note on Figures 6 and 7 the presence of 4 basins 1201, 1202, 1203 and 1204, 1301, 1302, 1303 and 1304 formed in hollow in the internal surfaces of each cup 120, 130. These basins are designed to be pressurized with fuel from channels 122, 132 to form hydrostatic bearings supporting the rotor 200 in its rotation around the axis O-O.

Le trajet en hélice-annulaire est schématisé sur la figure 3 et illustré partiellement plus en détail sur la figure 4.The helical-annular path is shown schematically in Figure 3 and partially illustrated in more detail in Figure 4.

Selon le mode de réalisation particulier illustré sur les figures annexées, le carburant qui pénètre dans la chambre de la pompe par l'entrée 134 atteint en premier lieu le canal 132 formé dans la coupelle inférieure 130, et de là gagne un passage 222 formé par les aubes 220, puis le canal 122 formé dans le flasque supérieur 120, un passage 232 formé par les aubes externes 230, le canal 132 formé par le flasque inférieur 130, puis à nouveau un passage 222 et ainsi de suite jusqu'à atteindre la sortie 124.According to the particular embodiment illustrated in the figures attached, the fuel which enters the pump chamber through entry 134 first reaches channel 132 formed in the cup lower 130, and from there gains a passage 222 formed by the vanes 220, then the channel 122 formed in the upper flange 120, a passage 232 formed by the external vanes 230, the channel 132 formed by the flange lower 130 and then again a passage 222 and so on until reach exit 124.

Pour garantir une position relative correcte des coupelles 120 et 130 (les passages 122 et 132 doivent être positionnnés exactement en regard), les coupelles 120 et 130 sont de préférence munies sur leur surface externe de moyens d'indexage ou détrompeurs. De tels moyens sont schématisés sur les figures annexées sous forme d'au moins une rainure 126, 136 ménagée dans la périphérie extérieure des coupelles 120, 130, lesquelles rainures sont destinées à être alignées lors de l'assemblage et de l'immobilisation relative des coupelles 120 et 130 pour recevoir une clavette. De même la bague 110 est de préférence munie d'une rainure externe 112 destinée à être alignée avec les rainures 126, 136 pour recevoir la clavette précitée.To guarantee a correct relative position of the cups 120 and 130 (passages 122 and 132 must be positioned exactly in look), the cups 120 and 130 are preferably provided on their external surface of indexing or polarizing means. Such means are shown schematically in the appended figures in the form of at least one groove 126, 136 formed in the outer periphery of the cups 120, 130, which grooves are intended to be aligned during assembly and the relative immobilization of the cups 120 and 130 to receive a key. Similarly, the ring 110 is preferably provided with a groove external 112 intended to be aligned with the grooves 126, 136 for receive the aforementioned key.

Selon une variante de réalisation, la bague 110 peut être intégrée à l'une des coupelles 120, 130.According to an alternative embodiment, the ring 110 can be integrated into one of the cups 120, 130.

Pour éviter que le carburant ne suive intégralement le rotor 200 dans son mouvement de rotation et aille ainsi trop rapidement de l'entrée 134 vers la sortie 124, les canaux auxiliaires 122 et 132 ménagés dans les coupelles 120 et 130 du stator 100 possédent des murets 127, 137 inclinés par rapport à une direction radiale. Ces murets 127, 137 imposent ainsi au carburant un trajet qui passe successivement par des paires de passages 222 et 232 radialement internes et radialement externes.To prevent fuel from fully following the rotor 200 in its rotational movement and thus goes too quickly from input 134 to output 124, auxiliary channels 122 and 132 provided in the cups 120 and 130 of the stator 100 has walls 127, 137 inclined to a radial direction. These low walls 127, 137 impose thus to fuel a path which passes successively through pairs of radially internal and radially external passages 222 and 232.

On a ainsi schématisé sur la figure 14 le trajet de filets de carburant dans la chambre de pompage en l'absence de tels murets et sur la figure 15 le trajet des mêmes filets de carburant grâce à la présence des murets 127, 137. L'homme de l'art comprendra à l'examen comparé des figures 14 et 15 que les murets 127 et 137 imposent une circulation du carburant par les passages 222 et 232 et par conséquent une montée en pression du carburant supérieure à la montée en pression susceptible d'être obtenue en l'absence de tels murets.We thus schematized in Figure 14 the path of nets fuel in the pumping chamber in the absence of such walls and on Figure 15 the path of the same fuel nets thanks to the presence of low walls 127, 137. Those skilled in the art will understand, on a comparative examination, Figures 14 and 15 that the low walls 127 and 137 impose a circulation of the fuel through passages 222 and 232 and therefore a rise in fuel pressure higher than the pressure increase likely to be obtained in the absence of such low walls.

De préférence les murets 127 et 137 sont formés de parois planes parallèles à l'axe de rotation O-O et inclinés par rapport à une direction radiale, comme on l'a indiqué précédemment.Preferably the walls 127 and 137 are formed of walls planes parallel to the axis of rotation O-O and inclined with respect to a radial direction, as previously indicated.

Il est ainsi défini entre deux murets 127 ou 137 adjacents inclinés par rapport à une direction radiale, des rainures 128, 138 aptes à guider le carburant entre les passages 222 définis par les aubes radialement internes 220 et les passages 232 définis par les aubes radialement externes 230.It is thus defined between two adjacent walls 127 or 137 inclined with respect to a radial direction, grooves 128, 138 suitable for guide the fuel between the passages 222 defined by the blades radially internal 220 and the passages 232 defined by the blades radially external 230.

La section droite des rainures 128, 138 peut faire l'objet de nombreuses variantes selon la géométrie de la paroi de fond de celles-ci. On peut ainsi concevoir des rainures 128, 138 de section droite triangulaire ou semi circulaire ou arrondie, notamment.The cross section of the grooves 128, 138 can be the subject of many variations depending on the geometry of the bottom wall thereof. It is thus possible to design grooves 128, 138 of triangular cross section or semi circular or rounded, in particular.

Cependant dans le cadre de la présente invention, de préférence, les rainures 128 et 138 présentent une section droite de contour rectangulaire , délimité par une surface de base perpendiculaire à l'axe de rotation O-O et deux flancs définis par les murets 127 ou 137.However, in the context of the present invention, preferably, the grooves 128 and 138 have a straight cross section rectangular, bounded by a base surface perpendicular to the axis of O-O rotation and two sides defined by low walls 127 or 137.

De préférence chacun des canaux auxiliaires 122 et 132 est muni de tels murets 127, 137.Preferably each of the auxiliary channels 122 and 132 is fitted with such low walls 127, 137.

Le pas des murets 127, 137 peut être identique à celui des aubes 220, 230. Cependant cette égalité de pas n'est pas obligatoire dans le cadre de la présente invention. The pitch of the walls 127, 137 may be identical to that of the blades 220, 230. However, this equality of pitch is not compulsory in the scope of the present invention.

Ces murets 127, 137 prévus sur les deux coupelles 120, 130 sont respectivement croisés entre eux, de préférence sensiblement à 45°, pour assurer un guidage du carburant correct. Ainsi si l'on observe les murets 137 prévus sur la coupelle inférieure 130, selon une direction allant de la coupelle supérieure 120 vers la coupelle inférieure 130, les murets 137 se déploient dans un sens anti-trigonométrique lorsque l'on se déplace radialement vers l'extérieur. Inversement les murets 127 prévus sur la coupelle supérieure 120 observés selon la même direction se déploient dans un sens trigonométrique lorsque l'on se déplace radialement vers l'extérieur.These low walls 127, 137 provided on the two cups 120, 130 are respectively crossed between them, preferably substantially at 45 °, to ensure correct fuel guidance. So if we observe the low walls 137 provided on the lower cup 130, in a direction going from the upper cup 120 to the lower cup 130, the low walls 137 deploy anti-trigonometrically when moving radially outward. Conversely, the low walls 127 provided on the upper cup 120 observed in the same direction deploy in a trigonometric direction when one moves radially towards outside.

Ainsi les murets 127 guident le carburant de la sortie d'un passage 222 radialement interne, vers l'entrée d'un passage 232 radialement externe, tandis que les murets 137 guident le carburant de la sortie d'un passage 232 radialement externe, vers l'entrée d'un passage 232 radialement interne.Thus the low walls 127 guide the fuel from the outlet of a passage 222 radially internal, towards the entrance of passage 232 radially external, while the low walls 137 guide the fuel of the exit from a passage 232 radially external, towards the entry of a passage 232 radially internal.

A titre d'exemple non limitatif :

  • le nombre de murets 127 et 137 est de 16 sur chaque coupelle 120, 130,
  • les rayons d'entrée et de sortie r5 et r6 des murets 127 et 137, sont de 13 et 16mm,
  • la hauteur des murets 127 et 137, considérée parallèlement à l'axe de rotation O-O est de l'ordre de quelques 10èmes de mm,
  • les angles d'entrée C1 et de sortie C2 des murets 127 et 137 sont compris entre -90° et + 90° par rapport à une tangente à la périphérie des canaux 122 et 132, en étant de préférence de l'ordre de + 45° par rapport à cette tangente,
  • les épaisseurs des parois formant les murets 127, 137 à l'entrée et à la sortie sont de l'ordre de 0,3 mm
  • les murets 127, 137 se raccordent à la paroi interne des canaux 122, 132 avec un congé de l'ordre de 0,2mm et
  • l'angle ouvert D défini entre deux murets adjacents 127 ou 137, à partir de l'axe O-O, est de l'ordre de 12°.
By way of nonlimiting example:
  • the number of low walls 127 and 137 is 16 on each cup 120, 130,
  • the entry and exit radii r5 and r6 of the walls 127 and 137 are 13 and 16mm,
  • the height of the walls 127 and 137, considered parallel to the axis of rotation OO is of the order of a few tenths of a mm,
  • the entry C1 and exit C2 angles of the walls 127 and 137 are between -90 ° and + 90 ° relative to a tangent at the periphery of the channels 122 and 132, preferably being of the order of + 45 ° with respect to this tangent,
  • the thicknesses of the walls forming the walls 127, 137 at the entrance and at the exit are of the order of 0.3 mm
  • the walls 127, 137 are connected to the internal wall of the channels 122, 132 with a fillet of the order of 0.2 mm and
  • the open angle D defined between two adjacent low walls 127 or 137, from the axis OO, is of the order of 12 °.

Selon une autre caractéristique avantageuse de la présente invention, le sommet des murets 127, 137 n'est pas coplanaire des surfaces internes des coupelles 120, 130, mais situé en retrait de ces surfaces internes, par exemple d'un intervalle de l'ordre de 0,1mm, comme on le voit par exemple sur la figure 17.According to another advantageous characteristic of the present invention, the top of the walls 127, 137 is not coplanar with the surfaces internal cups 120, 130, but set back from these surfaces internal, for example with an interval of the order of 0.1 mm, as can be seen for example in Figure 17.

Dans le cadre de la présente invention les aubes concentriques 220 et 230 sont incurvées et inclinées dans des sens respectivement opposées d'une série à l'autre.In the context of the present invention the blades concentric 220 and 230 are curved and tilted in directions respectively opposite from one series to another.

Ainsi selon le mode de réalisation particulier illustré sur les figures annexées, pour une rotation du rotor 200 dans le sens S et pour un sens d'hélice donné, les aubes internes 220 se déploient dans le sens S lorsque l'on se déplace de la coupelle supérieure 120 vers la coupelle inférieure 130. Et inversement les aubes externes 230 se déploient dans le sens opposé à S, c'est à dire dans un sens horaire, lorsque l'on se déplace de la même façon de la coupelle supérieure 120 vers la coupelle inférieure 130. L'inclinaison des aubes est inversée si l'un du sens de rotation S du rotor ou de l'hélice, est inversé.Thus according to the particular embodiment illustrated on the attached figures, for a rotation of the rotor 200 in the direction S and for a given helix direction, the internal vanes 220 deploy in the S direction when moving from the upper cup 120 towards the cup lower 130. And conversely the external vanes 230 are deployed in the opposite direction to S, i.e. clockwise, when moving in the same way from the upper cup 120 towards the lower cup 130. The inclination of the blades is reversed if one of the directions of rotation S of the rotor or propeller, is reversed.

On notera de plus que dans le cadre de la présente invention, de préférence les aubes 220, 230 ont leur concavité dirigée vers l'avant, en référence au sens de déplacement S du rotor 200.It will also be noted that in the context of the present invention, preferably the vanes 220, 230 have their concavity directed towards the front, in reference to the direction of movement S of the rotor 200.

Plus précisément encore les surfaces intrados 2200, 2300 et extrados 2202, 2302 des aubes 220 et 230 sont de préférence définies par des génératrices rectilignes, radiales par rapport à l'axe de rotation O-O et qui s'appuient sur des courbes lorsque lesdites génératrices sont déplacées le long de l'axe O-O.More precisely still the lower surfaces 2200, 2300 and upper surfaces 2202, 2302 of the vanes 220 and 230 are preferably defined by rectilinear generators, radial with respect to the axis of rotation O-O and which are based on curves when said generators are displaced along the axis O-O.

Sur les figures annexées, les bords d'attaque des aubes 220 et 230 sont référencés 2204 et 2304, tandis que les bords de fuite des mêmes aubes 220 et 230 sont référencés 2206 et 2306. Pour les aubes internes 220, les bords d'attaque 2204 sont situés sur la surface inférieure du rotor 200, tandis que les bords de fuite 2206 sont situés sur la surface supérieure du rotor 200. Inversement pour les aubes externes 230, les bords d'attaque 2304 sont situés sur la surface supérieure du rotor 200, tandis que les bords de fuite 2306 sont situés sur la surface inférieure du rotor 200. In the appended figures, the leading edges of the vanes 220 and 230 are referenced 2204 and 2304, while the trailing edges of same blades 220 and 230 are referenced 2206 and 2306. For the blades internal 220, leading edges 2204 are located on the lower surface of rotor 200, while trailing edges 2206 are located on the surface upper part of rotor 200. Conversely for external vanes 230, the leading edges 2304 are located on the upper surface of the rotor 200, while the trailing edges 2306 are located on the bottom surface of the rotor 200.

Selon le mode de réalisation illustré sur les figures 8a et 8b annexées, les surfaces intrados 2200 et 2300 et les surfaces extrados 2202 et 2302 ont des courbures identiques.According to the embodiment illustrated in Figures 8a and 8b annexed, the lower surface 2200 and 2300 and the upper surface 2202 and 2302 have identical curvatures.

Par contre selon le mode réalisation illustré sur les figures 9a et 9b, les surfaces intrados 2200 et les surfaces extrados 2202 des aubes internes 220 sont identiques entre elles, tandis que les surfaces intrados 2300 et les surfaces extrados 2302 des aubes externes 230 ont des courbures identiques entre elles, mais de rayon différent de celles des surfaces intrados 2200 et des surfaces extrados 2202 des aubes internes 220 précitées.By cons according to the embodiment illustrated in Figures 9a and 9b, the lower surface 2200 and the upper surface 2202 of the blades internal 220 are identical to each other, while the lower surface 2300 and the upper surfaces 2302 of the external vanes 230 have curvatures identical to each other, but of radius different from those of lower surface 2200 and upper surface 2202 of the internal vanes 220 above.

On notera par ailleurs que selon le mode de réalisation illustré sur les figures 8a et 8b, les aubes internes 220 et les aubes externes 230 ont des épaisseurs "e" identiques au niveau de leur bord d'attaque 2204, 2304 et au niveau de leur bord de fuite 2206, 2306 (On entend ici par "épaisseur" la dimension transversale "e" des aubes 220, 230 considérée dans un plan perpendiculaire à l'axe de rotation O-O).Note also that according to the illustrated embodiment in FIGS. 8a and 8b, the internal vanes 220 and the external vanes 230 have identical thicknesses "e" at their leading edge 2204, 2304 and at their trailing edge 2206, 2306 (We mean here by "thickness" the transverse dimension "e" of the vanes 220, 230 considered in a plane perpendicular to the axis of rotation O-O).

Selon le mode de réalisation illustré sur les figures 9a et 9b, les aubes internes 220 ont des épaisseurs e1 identiques au niveau de leur bord d'attaque 2204 et au niveau de leur bord de fuite 2206. De même les aubes externes 230 ont des épaisseurs e2 identiques au niveau de leur bord d'attaque 2304 et au niveau de leur bord de fuite 2306, mais l'épaisseur e2 des aubes externes 230 est différente (plus élevée) de celle e1 des aubes internes 220.According to the embodiment illustrated in FIGS. 9a and 9b, the internal vanes 220 have identical thicknesses e1 in terms of their leading edge 2204 and at their trailing edge 2206. Similarly the external blades 230 have identical thicknesses e2 in terms of their leading edge 2304 and at their trailing edge 2306, but the thickness e2 of the external vanes 230 is different (greater) from that e1 of the internal vanes 220.

Par ailleurs selon une autre caractéristique avantageuse de la présente invention la surface intrados 2200, 2300, au niveau du bord d'attaque 2204, 2304 est de préférence inclinée d'un angle compris entre 130° et 170° par rapport à un plan perpendiculaire à l'axe de rotation O-O , tandis que la même surface intrados 2200, 2300 au niveau du bord de fuite 2206, 2306 est de préférence inclinée de l'ordre de 90° par rapport à un plan perpendiculaire à l'axe de rotation O-O (c'est à dire que la surface intrados 2200, 2300 au niveau du bord de fuite 2206, 2306 est de préférence parallèle à l'axe de rotation O-O). Furthermore according to another advantageous characteristic of the present invention the lower surface 2200, 2300, at the edge 2204, 2304 is preferably inclined at an angle between 130 ° and 170 ° relative to a plane perpendicular to the axis of rotation O-O, while the same lower surface 2200, 2300 at the trailing edge 2206, 2306 is preferably inclined on the order of 90 ° relative to a plane perpendicular to the axis of rotation O-O (i.e. the surface lower surface 2200, 2300 at the trailing edge 2206, 2306 is preferably parallel to the axis of rotation O-O).

Sur les figures 8 et 9 annexées notamment, le bord d'attaque 2204, 2304 des aubes 220 et 230 est représenté effilé. Cependant en variante, comme illustré sur la figure 13, ce bord d'attaque 2204, 2304 peut être arrondi pour des questions de tenue mécanique.In Figures 8 and 9 appended in particular, the leading edge 2204, 2304 of the vanes 220 and 230 is shown tapered. However in variant, as illustrated in FIG. 13, this leading edge 2204, 2304 can be rounded off for reasons of mechanical strength.

A titre d'exemple non limitatif, le rayon d'un tel bord d'attaque arrondi peut être de l'ordre de 0,15mm.By way of nonlimiting example, the radius of such a leading edge rounding can be of the order of 0.15mm.

Par ailleurs sur les figures 8 et 9 annexées, chaque aube 220 et 230 est définie par une épaisseur de paroi "e" constante, considérée dans un plan perpendiculaire à l'axe de rotation O-O. Comme on le voit sur les figures, particulièrement sur la figure 9b, celà conduit cependant à un affaiblissement des aubes 220, 230 au niveau du bord d'attaque 2204, 2304. Pour renforcer les aubes 220, 230 on peut prévoir de définir une surface intrados 2200, 2300 parallèle à la surface extrados 2202, 2302 de sorte que les aubes 220 et 230 possèdent des dimensions transversales "Y" constantes sur toute leur largeur, considérées selon des directions générales perpendiculaires audites surfaces intrados 2200, 2300 et extrados 2202, 2302, comme on l'a illustré en variante sur la figure 12. Dans ce cas les aubes présentent des épaisseurs "e3" et "e4" différentes (considérées dans un plan perpendiculaire à l'axe de rotation), respectivement au niveau du bord d'attaque et au niveau du bord de fuite. A titre d'exemple non limitatif, cette dimension Y est de l'ordre de 0,3mm.Furthermore, in the appended FIGS. 8 and 9, each blade 220 and 230 is defined by a constant wall thickness "e", considered in a plane perpendicular to the axis of rotation O-O. As seen on the figures, particularly in FIG. 9b, this however leads to a weakening of the vanes 220, 230 at the leading edge 2204, 2304. To strengthen the blades 220, 230, provision may be made to define a lower surface 2200, 2300 parallel to upper surface 2202, 2302 of so that the vanes 220 and 230 have transverse dimensions "Y" constants over their entire width, considered in directions general perpendicular to the lower surface 2200, 2300 and extrados 2202, 2302, as illustrated in a variant in FIG. 12. In this case the blades have different thicknesses "e3" and "e4" (considered in a plane perpendicular to the axis of rotation), respectively at the leading edge and at the trailing edge. AT by way of nonlimiting example, this dimension Y is of the order of 0.3 mm.

Dans le cadre de la présente invention, de préférence les aubes 220, 230 ont des largeurs "L" (considérées parallèlement à l'axe de rotationO-O) identiques et constantes sur toute leur extension radiale. Cette largeur L des aubes 220, 230 est égale à l'épaisseur du rotor 200.In the context of the present invention, preferably the blades 220, 230 have widths "L" (considered parallel to the axis of rotation O-O) identical and constant over their entire radial extension. This width L of the vanes 220, 230 is equal to the thickness of the rotor 200.

En outre les aubes internes 220 et les aubes externes 230 ont de préférence même extension radiale.In addition, the internal vanes 220 and the external vanes 230 have preferably even radial extension.

Aprés de nombreuses recherches et après avoir éliminé notamment des solutions à base d'aubes planes radiales et parallèles à l'axe de rotation, d'aubes planes radiales et inclinées par rapport à l'axe de rotation, d'aubes en chevrons, (ces diverses solutions ne permettant pas une recirculation satisfaisante entre les deux séries d'aubes et/ou générant des phénomènes de cavitation), le Déposant a déterminé que les aubes incurvées et inclinées dans des sens respectivement opposées d'une série à l'autre donnaient le meilleur rendement.After much research and after eliminating in particular solutions based on flat radial blades parallel to the axis of rotation, of flat radial blades inclined relative to the axis of rotation, herringbone vanes, (these various solutions do not allow satisfactory recirculation between the two sets of blades and / or generating cavitation phenomena), the Applicant has determined that the blades curved and inclined in respectively opposite directions of a series to the other gave the best yield.

Selon le mode de réalisation illustré sur les figures 8a et 8b, mais non limitatif :

  • le nombre d'aubes 220 et le nombre d'aubes 230 est de 50,
  • le rayon interne r1 des aubes 220 est de l'ordre de 13 mm,
  • le rayon externe r2 des aubes 220 est de l'ordre de 14mm,
  • le rayon interne r3 des aubes 230 est de l'ordre de 15 mm,
  • le rayon externe r4 des aubes 230 est de l'ordre de 16 mm,
    ( les rayons r1, r2, r3 et r4 sont réduits chacun de 0,8mm dans le cas ou le rotor 200 comporte un anneau externe 260)
  • les largeurs radialement interne et radialement externe L des aubes 220 et 230 (qui correspondent à l'épaisseur du rotor 200) sont de l'ordre de 2mm,
  • les angles A1 et A2 des aubes 220 et 230, considérés dans un plan perpendiculaire à l'axe de rotation O-O sont de 90° par rapport à la périphérie du rotor 200,
  • l'angle B1 de la surface intrados 2200 des aubes 220 au niveau du bord d'attaque 2204 est de l'ordre de 140° par rapport à un plan perpendiculaire à l'axe de rotation O-O,
  • l'angle B2 du bord de fuite 2206 des aubes 220 sur la surface intrados 2200 est de l'ordre de 90° par rapport à un plan perpendiculaire à l'axe de rotation O-O,
  • l'angle B3 de la surface intrados 2300 des aubes 230 au niveau du bord d'attaque 2304 est de l'ordre de 140° par rapport à un plan perpendiculaire à l'axe de rotation O-O,
  • l'angle B4 du bord de fuite 2306 des aubes 230 sur la surface intrados 2300 est de l'ordre de 90° par rapport à un plan perpendiculaire à l'axe de rotation O-O,
  • l'épaisseur e de la paroi formant les aubes 220 et 230 est de l'ordre de 0,3mm,
  • l'épaisseur radiale de la bague support 250 est de l'ordre de 0,8mm.
According to the embodiment illustrated in FIGS. 8a and 8b, but not limiting:
  • the number of blades 220 and the number of blades 230 is 50,
  • the internal radius r1 of the vanes 220 is of the order of 13 mm,
  • the external radius r2 of the vanes 220 is of the order of 14mm,
  • the internal radius r3 of the vanes 230 is of the order of 15 mm,
  • the external radius r4 of the vanes 230 is of the order of 16 mm,
    (the radii r1, r2, r3 and r4 are each reduced by 0.8mm in the case where the rotor 200 has an outer ring 260)
  • the radially internal and radially external widths L of the vanes 220 and 230 (which correspond to the thickness of the rotor 200) are of the order of 2 mm,
  • the angles A1 and A2 of the vanes 220 and 230, considered in a plane perpendicular to the axis of rotation OO are 90 ° relative to the periphery of the rotor 200,
  • the angle B1 of the lower surface 2200 of the vanes 220 at the leading edge 2204 is of the order of 140 ° relative to a plane perpendicular to the axis of rotation OO,
  • the angle B2 of the trailing edge 2206 of the vanes 220 on the lower surface 2200 is of the order of 90 ° relative to a plane perpendicular to the axis of rotation OO,
  • the angle B3 of the lower surface 2300 of the vanes 230 at the leading edge 2304 is of the order of 140 ° relative to a plane perpendicular to the axis of rotation OO,
  • the angle B4 of the trailing edge 2306 of the vanes 230 on the lower surface 2300 is of the order of 90 ° relative to a plane perpendicular to the axis of rotation OO,
  • the thickness e of the wall forming the blades 220 and 230 is of the order of 0.3 mm,
  • the radial thickness of the support ring 250 is of the order of 0.8mm.

Selon le second mode de réalisation illustré sur les figures 9a et 9b :

  • le nombre d'aubes 220 et le nombre d'aubes 230 est de 30,
  • le rayon interne r1 des aubes 220 est de l'ordre de 13 mm,
  • le rayon externe r2 des aubes 220 est de l'ordre de 14mm,
  • le rayon interne r3 des aubes 230 est de l'ordre de 15 mm,
  • le rayon externe r4 des aubes 230 est de l'ordre de 16 mm,
    ( les rayons r1, r2, r3 et r4 sont réduits chacun de 0,8mm dans le cas ou le rotor 200 comporte un anneau externe 260)
  • les largeurs radialement interne et radialement externe L des aubes 220 et 230 (qui correspondent à l'épaisseur du rotor 200) sont de l'ordre de 2mm,
  • les angles A1 et A2 des aubes 220 et 230, considérés dans un plan perpendiculaire à l'axe de rotation O-O sont de 90° par rapport à la périphérie du rotor 200,
  • l'angle B1 de la surface intrados 2200 des aubes 220 au niveau du bord d'attaque 2204 est de l'ordre de 140° par rapport à un plan perpendiculaire à l'axe de rotation O-O,
  • l'angle B2 du bord de fuite 2206 des aubes 220 sur la surface intrados 2200 est de l'ordre de 90° par rapport à un plan perpendiculaire à l'axe de rotation O-O,
  • l'angle B3 de la surface intrados 2300 des aubes 230 au niveau du bord d'attaque 2304 est de l'ordre de 160° par rapport à un plan perpendiculaire à l'axe de rotation O-O,
  • l'angle B4 du bord de fuite 2306 des aubes 230 sur la surface intrados 2300 est de l'ordre de 90° par rapport à un plan perpendiculaire à l'axe de rotation O-O,
  • l'épaisseur e1 de la paroi formant les aubes 220 est de l'ordre de 0,3mm,
  • l'épaisseur e2 de la paroi formant les aubes 230 est de l'ordre de 0,3mm,
  • l'épaisseur radiale de la bague support 250 est de l'ordre de 0,8mm.
According to the second embodiment illustrated in FIGS. 9a and 9b:
  • the number of blades 220 and the number of blades 230 is 30,
  • the internal radius r1 of the vanes 220 is of the order of 13 mm,
  • the external radius r2 of the vanes 220 is of the order of 14mm,
  • the internal radius r3 of the vanes 230 is of the order of 15 mm,
  • the external radius r4 of the vanes 230 is of the order of 16 mm,
    (the radii r1, r2, r3 and r4 are each reduced by 0.8mm in the case where the rotor 200 has an outer ring 260)
  • the radially internal and radially external widths L of the vanes 220 and 230 (which correspond to the thickness of the rotor 200) are of the order of 2 mm,
  • the angles A1 and A2 of the vanes 220 and 230, considered in a plane perpendicular to the axis of rotation OO are 90 ° relative to the periphery of the rotor 200,
  • the angle B1 of the lower surface 2200 of the vanes 220 at the leading edge 2204 is of the order of 140 ° relative to a plane perpendicular to the axis of rotation OO,
  • the angle B2 of the trailing edge 2206 of the vanes 220 on the lower surface 2200 is of the order of 90 ° relative to a plane perpendicular to the axis of rotation OO,
  • the angle B3 of the lower surface 2300 of the vanes 230 at the leading edge 2304 is of the order of 160 ° relative to a plane perpendicular to the axis of rotation OO,
  • the angle B4 of the trailing edge 2306 of the vanes 230 on the lower surface 2300 is of the order of 90 ° relative to a plane perpendicular to the axis of rotation OO,
  • the thickness e1 of the wall forming the blades 220 is of the order of 0.3 mm,
  • the thickness e2 of the wall forming the blades 230 is of the order of 0.3 mm,
  • the radial thickness of the support ring 250 is of the order of 0.8mm.

Par rapport aux pompes classiques connues comprenant une seule série d'aubes, analogues par exemple aux aubes radialement externes 130, la pompe conforme à la présente invention permet d'améliorer sensiblement le rendement obtenu.Compared to known conventional pumps comprising a single series of blades, similar for example to radially blades 130, the pump according to the present invention allows to significantly improve the yield obtained.

En effet alors que la majorité des pompes classiques présentent un rendement généralement compris entre 13 et 16%, la pompe conforme à la présente invention, permet d'atteindre un rendement de l'ordre de 24%.Indeed while the majority of conventional pumps have a yield generally between 13 and 16%, the pump according to the present invention, achieves a yield of around 24%.

De préférence dans le cadre de la présente invention, toutes les pièces de la pompe, à savoir les coupelles 120 et 130, la bague 110 et le rotor 200, sont réalisées en matière plastique. En variante les coupelles 120, 130 peuvent être réalisées en métal, le rotor 200 au moins étant réalisé en matière plastique.Preferably in the context of the present invention, all the parts of the pump, namely the cups 120 and 130, the ring 110 and the rotor 200, are made of plastic. Alternatively the cups 120, 130 can be made of metal, the rotor 200 at least being made of plastic.

Par ailleurs on a illustré sous la référence 1380 un orifice de dégazage traversant la coupelle inférieure 130 et débouchant dans le canal 132 en aval de l'orifice d'entrée 134.In addition, reference 1380 illustrates an orifice of degassing through the lower cup 130 and opening into the channel 132 downstream of the inlet 134.

On a illustré sur la figure 16 un mode de réalisation préférentiel d'outil de moulage utilisé pour la réalisation du rotor 200 conforme à la présente invention. De préférence les canaux 222 et 232 formés entre les paires d'aubes 220, 230 adjacentes sont formés chacun par une paire d'excroissances complémentaires 310, 320 liées respectivement à chacune des coquilles de moulage.An embodiment has been illustrated in FIG. 16 preferred molding tool used to make the rotor 200 according to the present invention. Preferably channels 222 and 232 formed between the pairs of adjacent blades 220, 230 are each formed by a pair of complementary growths 310, 320 linked respectively to each of the molding shells.

Pour des aubes 220, 230 ayant un bord d'attaque effilé ou anguleux, ces excroissances 310, 320 sont de préférence adaptées pour définir des plans de joint situés sur les surfaces principales du rotor, orthogonales à l'axe de rotation O-O.For blades 220, 230 having a tapered leading edge or angular, these protuberances 310, 320 are preferably adapted for define joint planes located on the main surfaces of the rotor, orthogonal to the axis of rotation O-O.

En revanche, comme illustré sur la figure 16, pour un bord d'attaque arrondi, les excroissances 310, 320 sont de préférence adaptées pour définir des plans de joint P1, P2 qui coïncident respectivement l'un avec la génératrice du bord d'attaque situé dans le plan P3 passant par l'axe O-O tangent avec ce bord d'attaque 2204, 2304 et l'autre avec le bord de fuite 2206, 2306.However, as illustrated in Figure 16, for an edge rounded attack, the protuberances 310, 320 are preferably adapted to define joint planes P1, P2 which respectively coincide with one with the leading edge generator located in the P3 plane passing through the axis O-O tangent with this leading edge 2204, 2304 and the other with the edge leak 2206, 2306.

Selon une autre caractéristique avantageuse de la présente invention, les aubes 220, 230 et les canaux 222, 232 formés par celles-ci sont de préférence dimensionnés de sorte que les sommets 312, 322 des excroissances 310, 320 aient une largeur minimale La de l'ordre de 0,5mm, avec un angle de dépouille De minimal de 6°.According to another advantageous characteristic of the present invention, the vanes 220, 230 and the channels 222, 232 formed by them are preferably dimensioned so that the vertices 312, 322 of the protrusions 310, 320 have a minimum width La of the order of 0.5 mm, with a minimum draft angle of 6 °.

A titre d'exemple non limitatif, pour les aubes radialement internes 220 l'intervalle I1 entre deux aubes 220 adjacentes au niveau du bord de fuite 2206 peut être de l'ordre de 2,52mm, tandis que l'intervalle I2 entre deux aubes 230 radialement externes, au niveau des bords de fuite 2306 est de l'ordre de 2,94mm, la projection I3 et I4 des sufaces extrados 2202 et 2302 des aubes 220 et 230, sur un plan orthogonal à l'axe O-O étant respectivement de l'ordre de 1mm et 1,84mm.By way of nonlimiting example, for the blades radially internal 220 the interval I1 between two adjacent blades 220 at the level of the trailing edge 2206 can be of the order of 2.52mm, while the interval I2 between two radially external vanes 230, at the trailing edges 2306 is around 2.94mm, the projection I3 and I4 of the upper surface 2202 and 2302 of the vanes 220 and 230, on a plane orthogonal to the axis O-O being respectively of the order of 1mm and 1.84mm.

Bien entendu la présente invention n'est pas limitée au mode de réalisation précédemment décrit, mais s'étend à toutes variantes conforme à son esprit.Of course the present invention is not limited to the mode previously described, but extends to all variants conforms to his spirit.

Ainsi par exemple on peut concevoir dans le cadre de la présente invention des pompes multicellulaires, c'est à dire des pompes dans lesquelles la structure précitée est multipliée plusieurs fois sous forme de plusieurs chambres disposées fluidiquement en série (les chambres étant empilées coaxialement selon l'axe O-O) et logeant chacune un rotor 200 conforme aux dispositions précitées.So for example we can design in the context of present invention of multicellular pumps, that is to say pumps in which the above structure is multiplied several times in the form of several chambers fluidly arranged in series (the chambers being stacked coaxially along the axis O-O) and each housing a rotor 200 in accordance with the aforementioned provisions.

Selon le mode de réalisation illustré sur les figures annexées, il est prévu un nombre d'aubes radialement internes 220 égal au nombre d'aubes radialement externes 230. Cependant cette disposition n'est pas impérative. En pratique en effet le nombre d'aubes internes 220 peut être différent du nombre d'aubes externes 230. De préférence le nombre d'aubes tant internes 220 qu'externes 230 est égal à un nombre entier.According to the embodiment illustrated in the appended figures, a number of radially internal vanes 220 is provided equal to the number radially external vanes 230. However, this arrangement is not imperative. In practice, in fact, the number of internal vanes 220 can be different from the number of external vanes 230. Preferably the number both internal 220 and external vanes 230 is equal to an integer.

Claims (46)

  1. A turbine pump, in particular for a motor vehicle fuel tank, the pump comprising a stator-forming case (100) and a rotor (200) having blades (220, 230) mounted to rotate relative to the housing (100) and defining a pressure rise and flow path between an inlet (134) and an outlet (124), the rotor (200) possessing two concentric annular series of blades (220, 230), a radially inner series and a radially outer series respectively, the two series of blades (220, 230) being disposed radially on the inside and on the outside respectively of a ring (250), the radially inner series of blades (220) connecting the inside periphery of the ring (250) with the periphery of a central plate (210) such that the blades (220) define an annular series of peripherally-closed passages (222) passing through the thickness of the rotor (200), while a second ring (260) is disposed on the outside of the series of outer blades (230) such that said blades define an annular series of peripherally-closed passages (232) passing through the thickness of the rotor (200), the pump being characterized by the fact that the two series of blades are adapted to define a fuel path passing in alternation via the passages (222) defined by the radially inner blades and via the passages (232) defined by the radially outer blades (230) such that the path follows a generally helical configuration based on an annular envelope.
  2. A pump according to claim 1, characterized by the fact that the passages (222, 232) formed by the rotor (200) co-operate with auxiliary passages (122, 132) formed in the stator and which possess low vanes (127, 137) that are inclined relative to a radial direction so as to guide the fuel between the channels (222) defined by the radially inner blades (220) and the channels (232) defined by the radially outer blades (230).
  3. A pump according to claim 2, characterized by the fact that the low vanes (127) provided in a first auxiliary passage (122) disposed on one side of the rotor (200) are adapted to guide the fluid from the outlet of the radially inner blades (220) to the inlet of the radially outer blades (230), while the low vanes (137) provided in the second auxiliary passage (132) disposed on the other side of the rotor (200) are adapted to guide the fluid from the outlet of the radially outer blades (230) to the inlet of the radially inner blades (220).
  4. A pump according to claim 2 or claim 3, characterized by the fact that the channels (122, 132) are of a cross-section that presents a continuous curve of decreasing radius starting from the middles of the bottoms of said channels and extending to the free edges of said channels which coincide with the surfaces of the stator plate (120, 130).
  5. A pump according to any one of claims 2 to 4, characterized by the fact that the channels (122, 132) are of a cross-section that presents symmetry relative to a mid-plane orthogonal to the surfaces of the stator plates (120, 130).
  6. A pump according to any one of claims 2 to 5, characterized by the fact that the channels (122, 132) are of a cross-section that is substantially in the shape of a semi-ellipse.
  7. A pump according to any one of claims 2 to 6, characterized by the fact that it comprises auxiliary channels (122, 132) provided with low vanes (127, 137) in two stator plates (120, 130) respectively disposed on either side of the rotor (200).
  8. A pump according to any one of claims 2 to 7, characterized by the fact that the tops of the low vanes (127, 137) are set back from the inside surfaces of the stator plates (120, 130).
  9. A pump according to any one of claims 2 to 8, characterized by the fact that the tops of the low vanes (127, 137) are set back from the inside surfaces of the stator plates (120, 130) by a distance of about 0.1 mm.
  10. A pump according to claim 7, characterized by the fact that the low vanes (127, 137) provided on the two stator plates (120, 130) are mutually crossed.
  11. A pump according to any one of claims 2 to 10, characterized by the fact that the low vanes (127, 137) are formed by plane walls parallel to the axis of rotation O-O and inclined relative to a radial direction.
  12. A pump according to any one of claims 2 to 11, characterized by the fact that the grooves (128, 138) defined between the low vanes (127, 137) present a cross-section of rectangular outline.
  13. A pump according to any one of claims 2 to 12, characterized by the fact that the inlet and outlet angles C1 and C2 of the low vanes (127, 137) lie in the range -90° to +90°, preferably being about 45° relative to a peripheral direction.
  14. A pump according to any one of claims 1 to 13, characterized by the fact that the blades are curved with the two series being inclined in opposite directions.
  15. A pump according to any one of claims 1 to 14, characterized by the fact that the blades (220, 230) have their concave sides facing forwards, relative to the displacement direction of the rotor (200).
  16. A pump according to any one of claims 1 to 15, characterized by the fact that the two series of blades (220, 230) have their leading edges (2204, 2304) and their trailing edges (2206, 2306) situated on faces of the rotor that are opposite from one series to the other.
  17. A pump according to any one of claims 1 to 16, characterized by the fact that the intrados and extrados surfaces (2200, 2300 and 2202, 2302) of the blades (220, 230) are defined by rectilinear generator lines which are radial relative to the axis of rotation O-O and which follow curves when said generator lines are displaced along the axis O-O.
  18. A pump according to any one of claims 1 to 17, characterized by the fact that the intrados surfaces (2200, 2300) and the extrados surfaces (2202, 2302) of the blades (220,230) are of identical curvature.
  19. A pump according to any one of claims 1 to 17, characterized by the fact that the intrados surfaces (2200) and the extrados surfaces (2202) of the inner blades (220) are identical to each other, while the intrados surfaces (2300) and the extrados surfaces (2302) of the outer blades (230) are mutual of identical curvature but of a radius that is different from the radius of the curvature of the intrados and extrados surfaces (2200, 2202) of the inner blades (220).
  20. A pump according to any one of claims 1 to 19, characterized by the fact that the inner blades (220) and the outer blades (230) are of identical thickness "e" at their leading edges (2204, 2304) and at their trailing edges (2206, 2306), thickness being considered in a plane that is perpendicular to the axis of rotation O-O.
  21. A pump according to any one of claims 1 to 19, characterized by the fact that the inner blades (220) are of identical thickness e1 at their leading edges (2204) and at their trailing edges (2206), and the outer blades (230) are of identical thickness e2 at their leading edges (2304) and at their trailing edges (2306), but the thickness e2 of the outer blades (230) is different from the thickness e1 of the inner blades (220), thickness being considered in a plane that is perpendicular to the axis of rotation O-O.
  22. A pump according to any one of claims 1 to 19, characterized by the fact that at least one of the series of blades (220, 230) possesses a transverse dimension "Y" that is constant over their entire width, said dimension being considered along general directions that are perpendicular to the intrados and extrados surfaces (2200, 2300 and 2202, 2302).
  23. A pump according to any one of claims 1 to 22, characterized by the fact that, the intrados surfaces (2200, 2300) at the leading edges (2204, 2304) are inclined by an angle lying in the range 130° to 170° relative to a plane that is perpendicular to the axis of rotation O-O, while the same intrados surfaces (2200, 2300) at the trailing edges (2206, 2306) are inclined by about 90° relative to a plane that is perpendicular to the axis of rotation O-O.
  24. A pump according to any one of claims 1 to 23, characterized by the fact that the leading edges (2204, 2304) of the blades (220 and 230) are rounded.
  25. A pump according to any one of claims 1 to 24, characterized by the fact that the blades (220, 230) are of width "L" considered parallel to the axis of rotation O-O that is identical and constant over their entire radial extent.
  26. A pump according to any one of claims 1 to 25, characterized by the fact that the inner blades (220) and the outer blades (230) have the same radial extent.
  27. A pump according to any one of claims 1 to 26, characterized by the fact that the channels (222, 232) formed between adjacent pairs of blades (220, 230)
    are dimensioned so that each is formed by a pair of complementary projections (310, 320) from each of two mold shells respectively.
  28. A pump according to any one of claims 1 to 27, characterized by the fact that the channels (222, 232) formed between adjacent pairs of blades (220, 230)
    are dimensioned so that each is formed by a pair of complementary projections (310, 320) from each of two mold shells respectively, the tips (312, 322) of the projections having a minimum width (La) of about 0.5 mm, with a minimum clearance angle (De) of 6°.
  29. A pump according to claim 27 or claim 28, characterized by the fact that for blades (220, 230) having tapered or angular leading edges, the projections (310, 320) are adapted to define join planes situated on the main surfaces of the rotor, orthogonal to the axis of rotation O-O.
  30. A pump according to claim 27 or claim 28, characterized by the fact that for rounded leading edges, the projections (310, 320) are adapted to define join planes (P1, P2) which respectively coincide one with the generator line of the leading edge situated in a plane (P3) passing through the axis of rotation O-O and tangential to said leading edges (2204, 2304), and the other with the trailing edges (2206, 2306).
  31. A pump according to any one of claims 1 to 30, characterized by the fact that the stator (100) is formed by a ring (110) sandwiched between two cheeks or stator plates (120, 130), respectively a top cheek or stator plate and a bottom cheek or stator plate.
  32. A pump according to claim 31, characterized by the fact that the ring (110) is integrated in one of the cheek or stator plates (120, 130).
  33. A pump according to claim 31 or claim 32, characterized by the fact that, ignoring clearance, the rotor (200) is formed by a circular plate (210) of thickness that is equal to the thickness of the ring (110) and of maximum outside radius that is equal to the inside radius of the ring (110).
  34. A pump according to any one of claims 31 to 33, characterized by the fact that each stator plate (120, 130) possesses a semi-annular channel (122, 132) co-operating with the passages (222, 232) defined by the blades (220, 230) of the rotor (200).
  35. A pump according to claim 34, characterized by the fact that the segments (1221, 1322) of the semi-annular channels (122, 132) formed in the stator plates (120, 130) in which the pressure rise takes place, occupy an angle of about 270° about the axis of rotation.
  36. A pump according to claim 34 or claim 35, characterized by the fact that the segments (1224, 1324) of the semi-annular channels (122, 132) formed in the stator plates (120, 130) in which the pressure rise takes place, decrease in section towards the outlet (124).
  37. A pump according to any one of claims 34 to 36, characterized by the fact that the semi-annular channel (132) that is adapted to guide the fuel radially from the outside to the inside possesses a cross-section that is greater than that of the other semi-annular channel (122).
  38. A pump according to any one of claims 34 to 37, characterized by the fact that the radially inner radius of the channels (122, 132) formed in the stator plates (120, 130) is complementary to the minimum radially inner radius of the blades (220), while the radially outer radius of the channels (122, 132) formed in the stator plates (120, 130) is complementary to the maximum radially outer radius of the blades (230).
  39. A pump according to any one of claims 1 to 38, characterized by the fact that an inlet orifice (134) passes through the bottom stator plate (130) and opens out on one end of a channel (132) formed in said stator plate (130), while an outlet orifice (124) passes through the top stator plate (120) and opens out on the other end of a channel (122) formed in said stator plate (120).
  40. A pump according to any one of claims 1 to 39, characterized by the fact that the plates (120, 130) forming the stator (100) are provided on their outer surfaces with indexing means or keying slots (126, 136).
  41. A pump according to claim 40, characterized by the fact that the indexing means (126, 136) are formed by at least one groove formed in the outside peripheries of the stator plates (120, 130).
  42. A pump according to any one of claims 1 to 41, characterized by the fact that the stator plates (120, 130) possess troughs (1201-1204), 1301-1304) forming hydrostatic bearings.
  43. A pump according to any one of claims 1 to 42, characterized by the fact that at least the rotor (200) is made of plastics material.
  44. A pump according to any one of claims 1 to 43, characterized by the fact that a degassing orifice (1380) passes through a stator plate (130) and opens out in a channel (132) formed in said stator plate, downstream from an inlet orifice (134).
  45. A pump according to any one of claims 1 to 44, characterized by the fact that it comprises a plurality of chambers fluidicly disposed in series and each housing a rotor (200) in order to form a multi-cell pump.
  46. A pump according to any one of claims 1 to 45, characterized by the fact that it further comprises an electric motor capable of driving the rotor (200).
EP98943943A 1997-09-08 1998-09-08 Turbine pump with improved efficiency for motor vehicle fuel tank Expired - Lifetime EP1012479B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9711128 1997-09-08
FR9711128A FR2768192B1 (en) 1997-09-08 1997-09-08 IMPROVED TURBINE PUMP, PARTICULARLY FOR MOTOR VEHICLE FUEL TANK
PCT/FR1998/001917 WO1999013226A1 (en) 1997-09-08 1998-09-08 Turbine pump with improved efficiency for motor vehicle fuel tank

Publications (2)

Publication Number Publication Date
EP1012479A1 EP1012479A1 (en) 2000-06-28
EP1012479B1 true EP1012479B1 (en) 2002-12-18

Family

ID=9510848

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98943943A Expired - Lifetime EP1012479B1 (en) 1997-09-08 1998-09-08 Turbine pump with improved efficiency for motor vehicle fuel tank

Country Status (4)

Country Link
EP (1) EP1012479B1 (en)
DE (1) DE69810315T2 (en)
FR (1) FR2768192B1 (en)
WO (1) WO1999013226A1 (en)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
CN111561451A (en) * 2020-05-22 2020-08-21 扬州大学 Novel full tubular pump with auxiliary blades and design method thereof

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DE19941786B4 (en) * 1999-09-02 2008-11-20 Continental Automotive Gmbh feed pump
DE10019913A1 (en) * 2000-04-20 2001-10-25 Mannesmann Vdo Ag Pump esp. fuel pump or windscreen washer fluid pump for motor vehicles has driven shaft and rotor, one or both with elements for correct positioning
DE102016213547A1 (en) * 2016-07-25 2018-01-25 Robert Bosch Gmbh delivery unit

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FR954916A (en) * 1950-01-06
DE1144596B (en) * 1957-10-02 1963-02-28 Rudi Mueller Self-priming side channel centrifugal pump with a working chamber with an approximately circular cross-section
US5137418A (en) * 1990-12-21 1992-08-11 Roy E. Roth Company Floating self-centering turbine impeller
JPH0650280A (en) 1992-01-03 1994-02-22 Walbro Corp Turbine blade fuel pump
US5310308A (en) * 1993-10-04 1994-05-10 Ford Motor Company Automotive fuel pump housing with rotary pumping element
DE4336090C2 (en) 1993-10-22 2001-10-04 Bosch Gmbh Robert Unit for delivering fuel from a reservoir to the internal combustion engine of a motor vehicle
DE4341564A1 (en) 1993-12-07 1995-06-08 Bosch Gmbh Robert Unit for feeding fuel from tank to IC engine
DE4343078B4 (en) 1993-12-16 2007-09-13 Robert Bosch Gmbh Aggregate for conveying fuel from a storage tank to an internal combustion engine
US5452701A (en) 1994-05-23 1995-09-26 Walbro Corporation Turbine fuel pump with fuel jet
US5413457A (en) * 1994-07-14 1995-05-09 Walbro Corporation Two stage lateral channel-regenerative turbine pump with vapor release
EP0735271B1 (en) * 1995-03-31 2002-06-19 BITRON S.p.A. Motor vehicle fuel pump of peripheral type
US5596970A (en) * 1996-03-28 1997-01-28 Ford Motor Company Fuel pump for an automotive fuel delivery system
DE19622560A1 (en) * 1996-06-05 1997-12-11 Bosch Gmbh Robert Unit for delivering fuel from a reservoir to the internal combustion engine of a motor vehicle
US5702229A (en) * 1996-10-08 1997-12-30 Walbro Corporation Regenerative fuel pump

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111561451A (en) * 2020-05-22 2020-08-21 扬州大学 Novel full tubular pump with auxiliary blades and design method thereof
CN111561451B (en) * 2020-05-22 2021-08-06 扬州大学 Novel full tubular pump with auxiliary blades and design method thereof

Also Published As

Publication number Publication date
DE69810315D1 (en) 2003-01-30
FR2768192A1 (en) 1999-03-12
FR2768192B1 (en) 2004-01-23
DE69810315T2 (en) 2003-10-16
EP1012479A1 (en) 2000-06-28
WO1999013226A1 (en) 1999-03-18

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